Fluid pressure mechanism



May 18, 1948f QAQCARNAHAN 2,441,797

FLUID PRESSURE MECHANISM Filed July 9, 1943' 4 Sheets-Sheet 1 Jim/0W I1 an. mF/VAHA/V,

my 7.4 mm) Filed July 9, 1945 May 18, 1948.

4 Shets-Sheet 2 y 8, 1948. o. A. CARNAHAN e 2,441,797

' FLUID PRESSURE MECHANISM Filed July 9, 1943 4 Sheets-Sheet 5 gvvum'vbw Patented May 18, 1948 UNITED STATES PATENT OFFICE 2,441,797 FLUID PRESSURE MECHANISM Orson A. Carnahan, SyracusaN. Y. Application July 9, 1943, Serial No. 494,169

9 Claims.

In the past it has been customary in hydraulic mechanisms which are used either as pumps or motors to use some type of anti-friction bearings to carry the reaction loads resulting from piston thrust, and to depend on very accurate workmanship to insure proper valve timing in, order to prevent excessive pressure near the ends of the piston or plunger strokes.

Many diiferent types of constructions have been used for the purpose of carrying the excessive loads due to high pressures but all of the prior constructions have resulted in very heavy and cumbersome machines. In many other constructions parts have failed due to violent peak pressures which are caused by inaccurate valve timing. Inaccuracy of valve timing has been a result largely of the difficulty in securing precision in machining of parts and in the maintenance of the parts in proper relation due to continual wear.

An object of the invention is to provide a mechanism in which the piston forces are balanced to relieve the main crank shaft bearings of thrust loads; Another object of the invention is to provide improved mechanically operated balanced valves so as to still further'reduce the forces that other- Wise could be imposed on the crank shaft.

v A further object of the invention is to provide a valve mechanism that. will prevent excessive peak pressures at the ends of the piston strokes even despite slightl inaccurate valve timing due to minute inaccuracy in the machined parts, or due to the wear of the valve elements. F o

A still further object of the invention is-to provide an extremely light-weight hydraulic unit of rugged construction and of unusual durability, capable of operating continuously. at high speed and pressures without danger of bearing'failure. The various features of the invention can best be understood by reference to the accompanying drawings when viewed in light of the particular description that is to follow. In the drawings:

i Figurel is a cross sectional view of the pump or motor assembly taken along line l'-l of Figure Figure 2 is a cross sectional view taken along line 2- -2 of Figure 1;

Figure 3 is an enlarged cross sectional view of a single valve assemblymodified to include an auxiliary low pressure pump; and V Figure 4 is a cross-sectional view taken on line 44 of Figure 1; and

Figure 5 is a cross sectional view taken on line 5--5ofFigure1. j I

In the preferredv embodiment of-the invention the pump or motor mechanism is sealed in a'housingcomposed of two sections indicated by reference numerals 2 and 4 which are held together in a conventional manner, as by bolts. The mechanism within the housing includes a crank shaft 6 supported by main bearings 8 and I0 centrally located with respect to the casing. The crank shaft-6 includes three crank pins l2, I4, and [-6. Forming a part of the crank shaft 6 and bein located within the housing are four eccentrics I8, 20, 22, and 24. V

. Three largepl ne'e s 26 are arranged about the large center pin M in a plane perpendicular to the axis of the crank shaft and in equally spaced relation with respect to each other. The plungers 2i? are held against the center pin M by means of two sectional rings 28 having three sections each and which bear upon flanges 30 extending from the wall of the plungers at the base of each thereof. Each of the plungers reciproca-tes in a cylinder 32 which in turn is mounted for oscillation on a cylinder head 34 by means of bands 35 extending from the outer ends of the cylinders 32 into bearing contact with the cylinder head 34.

The three cylinder heads 34 together with cooperating valve chests 36 and 38 are held in sym-. metrically spaced relationship about the crank shaft 6 by housingsections 2 and 4, forming a tightly sealed assembly. Obviously gaskets and packings may beused for effecting tight seals wherever required throughout the assembly.

As shown in Figure 1 of the drawing, the housing sections 2 and 4 are provided with passageways 40 and 42, respectively. These passageways are formed within the periphery of the respective sections 2 and 4 and they communicate with each of the cylinder heads 34 and valve chests 36 and 38 to form a continuous passage between their respective peripheral portions 40 and 42. The passages 40 and 42 are provided with external connecting means 44 and 46 whereby fluid may enter and be discharged from the fluid pressure mechanism. The valves operating to control the motor are of identical construction and their description will follow hereinafter.

A set of three small plungers 48 each having one-half the area of one of the plungers 26 are held to the crank pin l2-by sectional rings 50 which bear against flanges 52 extending from the wall of the plungers 48. A similar set of three small plungers 54 also havingone-half the area of the plungers 2-6 are held to the crank pins [-6 by sectional rings 56 which bear against outwardly extending'flanges 58 at the base of the plungers.

A plunger and its cooperating cylinder may be referred to herein as a plunger-cylinder combination, and a plurality of such plunger-cylinder combinations attached to any given crank pin may be designated herein as an aggregate.v

Plungers 48 reciprocate in'cylinders 60 andthe crank shaft 6 and diametrically opposed. to cylinder heads as by the housing sections 2 arm 4Q A tightly sealed assemblies being formed. thereby i between passages 48 and 42. k

It will be observed from an examination of Figure 1 that the two valve chests 36 and 38 are associated With each of the large cylinders 32 and that the two valve chests $6 and 68' are associated with each pair of smaller cylinders 66 and 62. Tocon trol the flow of fluid through each of the valve chests 36 and 38, valve assemblies 10 and i2 are provide'd'. The valve assemblies Ill and 12 are cperated ,by the eccentricsfll and 22 which rotate with the crank shaft 6. The valve chest The cylinder H heads 64 and valve chests 66 and ;68 are held symmetrically spaced relationship relative to the tion between the duct 40 and the cylinder head 64. The outer portion of the passage H8 is in communication with an auxiliary valve I20 by means of bleed port I22 and auxiliary valve port #24; The inner end of the auxiliary valve I20 is provided with passage I26.

In similar fashion the .valve ea has formed therein a fluid passage I28'afiording communication between the cylinder head 64 and the annular ductfll The valve I02 operating in the valve body 6'3 includes an auxiliary valve I30 whichlconimui'iicates with the main valve passage I2 8 by. way of a bleed port I32 and passage I 34 at the'outer end of thelauxiliary valve. The in- 36 is provided with the reciprocatingvalve 10 which, in turn, includes an auxiliary valve I4, both valves together reciprocating inshore pro vided "Within the valve chest; The valve Ill and its auxiliary valve 14 are reciprocated by the motion of the eccentric 20 transmitted through the eccentric strap 15 and the hinge pin l3. i

In a similar manner the valve 12 in theva-lve chest 38 is provided with an auxiliary valve 89 both of which reciprocate in a bore provl'ded-in the valve chest. The valve 72 and its auxiliary valve 80 are reciprocated by 'the motion of the v 1 eccentric 22 transmitted-through the eccentric strap 82 and ahinge pin 'BS. 7

Operation of "the valve 70, the auxiliary valve la, the valve I2, and the auxiliary valve -'8'I control the if-low of fluid into and out'of the cylinder during the reciprocation of the plungers -l't as will be'more ifully explainedhereinafter. v

The valve body 36 is provided with passages 84 comma icating; with opposite "sides of the ;valve TF3. A of the 'pas'sa 'esfas extend into the outer end or the valve stems r communication With a port tewithinth auxiliary valve [4. The auxiliary valve liaise includes ports "910 "communicating with the inner-passage i8'4'. s V. H v

The valve body sa es passages "92 extending from cease s des mete r P l id e i c e flew of fluid through the valve 72; 1 The valve body '38 also includes a bleed passage 94 communicating with an inner-part es in the 'auxiliary valve '80, 3 the auxiliary valve having a port '98 communi cating'with one of the main valve pol'tsSZ. Each-of the valve assemblies 66 and 68 that cooperate with the "cylinder headed-is provided with valve mechanisms I62 andlllg, respectively. The valve iliilis reciprocated within the valve bodyfi Qthrough a strap H74 and a hinge pin I 06, the strap liil ljencircling the eccentric 1'8 'andreceivingitsidriving fprce therefrom.

The valve. I92 receives its reciprocating motion.

from the crank shaft eccentric 24 through the connecting strap BB and the hinge pin H 0. The valves 'liie and 102 "control the jilow of fluid to and irom thefcylinders '60 and 62 by way of the cylinder head 15 .5 and; cylinder ports I I 2 and 15M;

respectively. The valves "19 and 72 "control 'the ed passagefifi communicating with one ner end of the auxiliary valve is provided with passage I36. r r

The general" "construction of 7 the valves throughout the assembly is substantiailyfidenti cal and a full understanding of the construction can be secured by referring to'Fi ure 3 of the drawing wherein a slightly modified form of the valve construction is illustrated." :in Figure 3 of the drawing the valve .:comprises a cylindrical member 158. liavil'l'g a reduced sect-ion 152 in its central .pbrtion'whi'ch operates Within the bore 1'54 provided in the valve chest I155; :One end of the cylindrical member I5!) isconnected to an eccentric strap I58 by a removable hinge pin I60 which serves as a connection between the eccentricstrap' I 58 andth'e valve member I523. The cylindrical valve member IE2 is provided with a cavity' I64, the inner end of which is provided with a'valv'e seat I68. Theicavity IE4 is closed at its outer. end by spice 17B forming "a closure therefor and constituting a'n auxiliary valve mechanism operable through a ball valve I12. The :ball valve "I12 is provided within the cavity I64 an'dis biased against the valve seat' I68 by valve spring I'M. lin theembodiment shown in Figure 3 of the draw'irrgtlie, valve I12 comprises a ball closure which is biased against the valve seat I68 by a coil compression spring I14 although itfiis contemplated that other types of valve may "be employed within the scope of the invention.

The valve member I50 liaszfor me'd therein peripheral grooves 176 :and ['78 located within the -area 'of the auxiliary valve body. The :groove I18 communicates with' the interior of cavity I 64 by way er a passage I and-gas :shown in Figure 3., this .gr'oov'e is'positioned adjacent the end of the cylindrical:valve member I58. The groove H6 communicates "with :the interior "of the cavity I 64 -by 'way *or a'passage 1 82, valve seat ms, and the "spring pressed ball 'clos'ure 1E2; When the valve ball 1 12' is 'seated'dn the valve seat 168 "under tension fbf the spring- 114, the passage 182 between groove 'I'I li and away It is closed. As showninl igure 3, the groove W6 is positioned-in- 'termedia'te'the groove 1T8 anaftnetredaced portion ='I:5'2 'of thereciprocating valve member I 50. In 'order to f a ili'tate "the new 62 fluid into the valve cavity $64 by way of the passage I80, the valve a. body "I56 is provided withe -groove I84 adapted to register with the peripheral groove 118 111the-auxilia'ry'valve.

The valve body I56 includes poits-letexten mg through-the valve by wa'y of the reduced body I 52 of the reciprocatingvalve rneinber its. Thegpassage I86 is in communication with the auxiliary valve cavity 1 64 *by way of "a lbl'e'edpo'rt I188.

Insofar as. described, the valve assembly shown in Figure 3 corresponds to those more generall shown in Figure .1 of the drawings. "In the concluded aTI'l auxiliaryvalve chest as'sfilbly'that'may be used in conjunction with one or more of the regular valve assemblies whenever an auxiliary low pressure'pump is required. For example, the intake and discharge fittings thereof may be connected with suitable ports in the main casing, adapting the auxiliary pump to sump drainage or pump priming purposes. The auxiliary low pressure valve assembly consists of a valve chest I90 which forms a closure for the outer end of the bore I54 in the main valve body I55. The valve chest I90 is provided with an intake fitting I92 having an intake passage I94 and avalve seat I 96, An intake valve I98 is biased against the valve seat I90 by a valve spring 200. The auxiliary valve chest I90 also has a passage 202 connecting the intake passage I94 with the chamber formed at the end of the valve body I50 by reason of the auxiliary valve I90. The auxiliary valve chest I90 includes a discharge passage 204 controlled by a discharge valve 206 that is pressed against its valve seat 208 under the pressure of the valve spring 2I0. The discharge passage 204 has a discharge fitting 2| 2 for connection with an exit line.

In my application for patent Serial No. 302,587, filed November 2, 1939, now Patent No. 2,347,663,- of which this application is a continuation-inpart, I have disclosed and claimed a fluid pressure bearing of which certain features have been embodied in this invention. In that application I have disclosed a bearing structure consisting of a cylinder, a slidable plunger in telescopic assembly with the cylinder, a bearing surface at one end of the plunger in mating contact with a supporting surface. In that application the head on one end of the plunger bears a relation to the area of the bearing surface so that fluid under pressure passing through a passage between the plunger head and the bearing surface is trans-. mitted to the mating bearing surfaces to maintain a film of fiuid therebetween that remains constant for whatever variation may occur in the load imposed on the mechanism.

In the present instance the plungers throughout the pump have been constructed in accordance with the teaching of my prior application and in accordance therewith the plunger 26 has a passage 2I4 in the base thereof for admitting fluid under pressure to the inner surface thereof thereby providing a lubricating and supporting film between the plunger and the crank bearing. In similar fashion the plungers 48 and 54 are provided with passages 2I6 and 2I8, respectively, thereby admitting fluid under pressure to the bearing surfaces between the inner faces of the plungers and the engaging surface of the crank shaft.

The fluid pressure mechanism may be operated either as a pump or a motor and in either direction. For example, if fiuid under pressure is applied at the intake connection 44 (Figure 1), the pressure will be transmitted through passages 40 to ports II8, I22, 84, and 80. By reference to Figure 2, it will be seen that'port 84 is closed by the valve I0, port 86 is open through valve ports 88 and 90, but valve port 88 is closed against fiow into the cylinder 32 by the auxiliary valve I4. Since all of the valves of each set of three are operated from the same crank shaft eccentric, it will be obvious that their position will be changed in timed relation with respect to each other and in this regard it is to be noted that ports 84' and 86' in the second valve of the group of three are both closed by valve I0, but that the port 84" in the thirdvalve of the group open to its corresponding cylinder. The high pressure liquid entering through port 84" to its corresponding cylinder causes a rotation of the crank shaft 6 in a counter-clockwise direction.

Reverting again to the valve system illustrated in Figure 1 of the drawing, as the crank shaft rotates, the motor action of the cylinders and valves shown in cross section in that figure is as follows: Plungers 48, 26, and 54 start out of their respective cylinders thereby tending to produce a vacuum in the cylinders 60, 32, and 02. The rotary motion of the crank shaft 6 iscommunicated to all valves through the action of the eccentrics, I8, 20, 22, and 24, the corresponding straps,I04-, I6, 82, and I08, and the hinge pins I86, 78, 83, and 'I III. The valve motion produced through these instrumentalities is effective first to close the auxiliary ports 94 and I32 and then to'open'the main ports H8 and 84. The high pressure fiuid entering through port I I0, cylinder head passages H2 and H4 acts on plungers 48 and 54, and crank pins I2 and IS. The forces on plunger '40 .and 54 are transmitted to the crank pins I2 and I6 through the supporting lubricating films as herein described. At the same time high pressure fluid entering through port84 and cylinder head passage II6 acts on the larger plunger 26. and its crank pin I4. The force on plunger 26 is similarly transmitted to crank pin I4 by the supporting lubricating film between the respective surfaces. Since the force acting on theicl'ank pin I4 isequal to the sum of the forces acting on cran-k pins I2 and I0, there is no component to becarried by the main bearings 8 and I0.

.Narthe end of the stroke, valves I00 and 10 close ports H8 and 84, again forming a vacuum in cylinders 48, 28, and 54. Valves I2 and I02 next open ports 94 and I32 just before the'iend of the stroke. At the beginning of the'return or discharge stroke any excess pressure will be relieved through the auxiliary valves 80 and I30, the valves I20 and I l being inoperative due to the check valve action. Just after the beginning of the return stroke, valves I00 and I0 close the auxiliary valve ports I22 and 80 which in no way affects theaction as a motor.

T Valves I2 and I02 next open main ports 92 and I28 for free discharge through passage 42 and connection 40. Near the end of the discharge stroke valves 72 and I02 closemain ports 92 and I28 and the remaining discharge is through auxunique valve mechanism, a slight inaccuracy in valve timing cannot result in excessive peakpressures near the ends of the strokes or in ajiloss of pressure due to both intake and discharg'valves being open at the same time. It will also be noted that the power strokes of the multiple cylinder mechanism give a continuous torque whichvaries slightly in magnitude much like a multiple cylinder, gas or steam engine. By increasing the number. of cylinders, the torque may'bemade even more uniform.

Assuming the crank shaft 0 is rotated in a clockwise direction, the mechanism functions as a pump and the action of thecylindersand valves 7 in cross section Figilifl'e 1 as 6116" s; As the plungers 48, 2B, and 54 start on their sue tron strokes with main ports Ha, 84,92, and I28 all closed and with auxiliary ports I24, 88, 06, and I34ope'n except for the auxiliary valves I20, I4; 80, and I30, which prevent fluid from entering the cylinders 48, 2e, and 54, a vacuuni will be formed at the beginning of'the stroke. valves I and H3 first close ports I24 and 88. Thenvalves I2 and I02 open the main ports92 and I28 permitting fluid to enterthrough connection 46, passage 42, ports 92 and I28, eyunder head openings H2, H4, and H6. Valves I2 and I02 close the main ports 92 and I28 cutting off admis-' sion to cylinders 48, 26, and 54, so thata vacuum will be formed just before the end of the stroke.

Valves I00 and next open auxiliary ports I24 7 and 88 to passages I22 and 86 which are inoperative for the remainder of the stroke due to the auxiliary valves I and '14. On the return or discharge stroke, the vacuum is first relieved and then a very small volume of fluid may be dis-' charged to the suction side before valves 12 and I02 close the auxiliary ports 96 and I34, the dis charge being through auxiliary valves I20 and I4. Valves I00 and I0 next open the main ports H8 and 84 for free discharge through ports H8 and 84, passage 40 and connection 44. the end of the discharge stroke, valves I00 and- 10 close the main ports I I8 and 84 when discharge will be through the auxiliary valves I20 and 14,- ports I22 and 86,- passage 40 and connection 44. Just before the end of the stroke valves 12 and I02 open the auxiliary ports 96 and I34 allowing the last of the discharge to return to thesuctlon' Just before 7 side'of the mechanism. The foregoing describes V a complete revolution or cycle of the mechanism and it can be seen therefore that dueto the over lapping of the auxiliary valve port openings, there may be a slight loss in volumetric efficiency. However, the auxiliary valves prevent the possibilityof excessivetpeak pressures due to improper valve timing and therefore eliminate one of-rthe' serious defects in mechanisms of this kind as known heretofore. 1

Having now fully described the invention, whatisclaimed as new and that for which Letters Patent is desired is the following:

1. In combination, a crank; shaft having at least three throws, at'least two of said throws constituting a set being displaced 180 with respect to the remainder, a plurality of plunger andv cooperating cylinder combinations constituting an aggregate corresponding to each, of said throws; a manifold for each plunger-cylinder combination of each aggregate, each of said plunger-cylinder combinations being connectedat one end thereof to its corresponding throw' and the other end of each thereof being mountedfor oscillation on its corresponding manifold whereby rotation of said crank shaft is accom-; panied by angular oscillation of each plungercylinder' combination and relative reciprocation betweenltlie plunger and cylinder o'i'eacli' coin-r '2. n1 efii-biiiatien, a crank shaft having three throws; twe tr'saie throws constituting a set and hem isfalaced 180 with'respec't to the third w; a plurality of plunger and cooperating cylinder combinations constituting an aggregate esrreseeneing to each of said throws, a manifold rereaen iifiifigiicylindei combination of each agereg' te, each or said piunger-"cyiinder combinations being cen-nected at one en the eof to its .ccrr'espondmg throw and the other end of each thereof Being friotinted-fo'roscillatioii on its eoffes'pefiding' manifold wherebyrotation of said crane shaft is accompanied by' angular oscilla tieii of each piunger=cy1inder combination and relative reciprocation between the plunger and cylinder ofeac'n cornbination'passages through which fluid may enter and leave eacho'f said cyl'ii-iders, valves for controlling the ilo'w'oi fluid into and out of said cylinders'sa-id passages being connected to a header, the effective working area of the piunger' cylinder aggregatesconnected to said set of throws being substantially equal to the effective working area of the plunger-cylinder aggregate connected to the l"displaced traits, and the angle of oscillation of each of eylinder combination of each aggregate-each of said piunger-cylinder combinations being cone nected at one end th'erebf to its corresponding throw a-nd the' other end of each thereof 'bein Ino'untecl for oscillationon its corresponding mam-fold whereby rotation of said crank shaft is accompanied by. angular oscillation of each plung-er-'- cylinder combination an relative reciprocation bet-ween: the plunger and cylinder of each combination passagesthrough which fluid may enterand leave each of said; cylinders, valves for controlling theflow of fluidinto and out of said cylinders, said; passages being connected to' a; header,-

effective" working area of the plunge-rmylindera'ggregates; connectedto said set ofthrows being substantially equal to the eifectiveworking area of the' plunger-oylinder aggregate connectedto the displaced intermediate'throw; and the angle of dscillation of each; ofsaid plunger-cylinder aggregatesbeing equal to each othenthereby balancing the forces of translation.

constituting a set being displaced l; 8( )-.w

4 1m; combiner-tibiae crank shaft having at least three throws, at least throws We??? e man 3. coopeilatirrg' cylindcr' combinations constituting anaggregate corresponding to each of said combination of each aggregate, each, of said plunger-cylinder combinationsbeing connected at one endthereof to itscorresponding throw 7 and the othenendof' each thereotbeing mounted is a'c maturation passages tnrtu'gn which fluid? may enter and leave each of said cylinders, said passages being connected to a header, the effective working area of the plunger-cylinder aggregates connected to a set of throws being substantially equal to the effective working area of the plunger-cylinder aggregate connected to the 180 displaced throw, the angle of oscillation of each of said plunger-cylinder aggregates being equal to each other, thereby balancing the forces of translation, valve mechanism controlling the flow of fluid through said passage, and means interconnecting said valve mechanism and said crank shaft whereby said mechanism is positively operated when said shaft is rotated.

5. In a fluid pressure device, a crank shaft having valve actuating eccentrics, a fluid manifold disposed in spaced parallel relation with respect to said crank shaft, a piston and cylinder combination for causing the flow of fluid through said manifold, one end of said combination being attached to said crank shaft and the other end thereof being attached to said manifold, an inlet valve for controlling fluid flow into said pistoncylinder combination, a discharge valve for controlling fluid flow out of said piston-cylinder combination, a valve actuator interconnecting each of said valves and its respective eccentric, said'inlet valve having a port that opens after said piston has started on its intake stroke and closure before said piston has reached the end of its intake stroke, said discharge Valve having a port operative after said inlet port of said firstnamed valve is closed and which opens before said piston has started its discharge stroke and closes after said piston has reached the end of its discharge stroke and before said inlet port of said first-named valve opens. l l

6. In a fluid pressure device, a crank shaft having a throw and a valve actuating eccentric, a fluid manifold disposed in spaced parallel relation with respect to said crank shaft, a piston and cooperating cylinder, one of which is attached to said crank shaft and the other of which is attached to the manifold, a valve mechanism for controlling fluid flow through said manifold, including an inlet valve, an actuator interconnecting said valve and said eccentric, said valve having an inlet port that opens after said piston has started on its intake stroke and closes before said piston has reached the end of its intake stroke, a second valve controlling discharge from said manifold, said valve having a discharge port operative after said inlet port is closed and which opens before said piston has started its discharge stroke and closes after said piston has reached the end of its discharge stroke and before said inlet port opens, and means for operating said second valve in said sequence.

7. In a fluid pressure device, a crank shaft having a valve actuating eccentric, a fluid manifold disposed in spaced parallel relation with respect to said crank shaft, a piston and cooperating cylinder, one of which is attached to said crank shaft and the other of which is'attached to the manifold, said piston and cylinder combination constituting a pump operable by said crank for causing the flow of fluid through said manifold, a reversible flow valve mechanism for controlling fluid flow through said manifold, including a valve for controlling fluid flow through one end of said manifold, an actuator interconnecting said valve and said eccentric, said valve having a port that opens after said piston has startedon its intake stroke and closes before said piston has reached the end of its intake stroke, a second valve controlling fluid flow through the other end of said manifold having a port operative after said first named port is closed and which opens before said piston has started its discharge stroke and closes after said piston has reached the end of its discharge stroke and before said first named port opens, and means for operating said second valve in said sequence.

8. In a fluid pressure device, a crank shaft having a pair of valve actuating eccentrics, a fluid manifold disposed in spaced parallel relation with respect to said crank shaft, a piston and cooperating cylinder, one of which is attached to said crank shaft and the other of which is attached to the manifold,,a reversible flow valve mechanism including a pair of valves for controlling fluid flow through said manifold, valve actuators interconnecting said valves and said eccentrics, each of said valves having a main port and an auxiliary port, the main ports being operative either as intake or discharge ports, the auxiliary ports being operative only as discharge ports, said valves being so arranged and operated that the main ports open after the piston has started its stroke and close before the end of the stroke, and the auxiliary ports open only after the main ports are closed and before the piston has started its discharge stroke and close after the piston has reached the end of its discharge stroke and before said main ports open,

9. In a fluid pressure device, a crank shaft having a pair of valve actuating eccentrics, a fluid manifold disposed in spaced parallel relation with respect to said crank shaft, a piston and cooperating cylinder, one of which is attached to said crank shaft and the other of which is attached to the manifold, a reversible flow valve mechanism including two valves for controlling fluid flow through said manifold, a pair of valve actuators interconnecting said valves and said eccentrics, one of said valves having an inlet port that opens after said piston has started ,on its intake stroke and closes before said piston has reached the end of its intake stroke, and the other of said valves having a discharge port operative after said inlet port is closed and which opens before said piston has started its discharge stroke and closes after said piston has reached the end of its discharge stroke and before said inlet port opens.

ORSON A. CARNAHAN.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 439,792 Storey Nov. 4, 1890 1,239,059 Sundh Sept. 4, 1917 1,416,314 Atkins May 16, 1922 1,557,434 Demarest Oct. 13, 1925 1,990,263 Benedek Feb. 5, 1935 2,013,473 Read Sept. 3, 1935 2,151,402 Burch Mar. 21, 1939 2,307,374 Johnston Jan. 5, 1943 2,347,663 Carnahan May 2, 1944 FOREIGN PATENTS Number Country Date 21,119 Norway Feb. 6, 1911 261,984 Great Britain 1926 466,180 Great Britain May 21, 1937 

